Clear buck pressing machine



March 1970 v. w. TUCKER ET AL 3,500,567

CLEAR BUCK PRESSING MACHINE I Filed March 26, 1969 3 Sheets-Sheet 1 FIG. I.

FIG. 2

INVENTORS VINCE/VT K- TUCKER MAI/EL 7: 09/170 ATTORNEYS 5 0mm: 5 mmmz n L- i M March 17, 1970 v. w. TUCKER ET AL 5 5 CLEAR BUCK PRESSING MACHINE Filed March 26, 1969 3 Sheets-Sheet 2 FIG. 3.

INVENTORS I/IVCEAI' I H CKIR PAN/EL 7. (ll/l 701V BY EDWAkD 15' VA/VDALL ATTORNEYS March 17, 1970 v, w, TUCKER ET AL 3,500,567

CLEAR BUCK PRESSING MACHINE Filed March 26, 1969 v 3 Sheets-Sheet 3 ATTORNEYS United States Patent 0 3,500,567 CLEAR BUCK PRESSING MACHINE Vincent W. Tucker and Daniel T. Chilton, Cape Elizabeth, and Edward F. Vandal], Falmouth Foreside,

Maine, assignors to Ametek, Inc., New York, NY.

Filed Mar. 26, 1969, Ser. No. 810,758 Int. Cl. D06f 71/08 U.S. Cl. 3835 18 Claims ABSTRACT OF THE DISCLOSURE A pressing machine of the type including a stationary buck and movable head wherein said head is initially disposed in a clear buck position spaced rearwardly of the buck of the pressing machine and in a position wherein the buck is free of any obstruction to enable the work to be draped thereon, with an actuating mechanism and control being provided for moving the buck to a standoff position in spaced confronting relation above and aligned with the buck from which standoff position the head moves downwardly, first into a contact or zero pressure position and then into a pressure-applying position.

The present invention relates to pressing machines and controls and, in particular, to a pressing machine of the clear buck type, including improved actuating and control mechanisms.

The well-known garment-pressing machine comprises a frame, including a work table, a stationary buck mounted on the frame and a movable pressing head pivotally mounted on the frame for movement relative to the buck from an open position removed from the buck into a pressure-applying position in high pressure engagement with the buck. Machines of this type have been constructed wherein the open position is a so-called clear buck position in which the movable head is spaced rearwardly behind, and usually below the level of the buck such that the operator has unobstructed access to the stationary buck for draping the work thereon, Further, it is known to provide a garment-pressing machine wherein in addition to the open head position, be it a normal clearance position wherein the head is spaced above the buck or a clear buck position wherein the head is disposed behind the buck, the head is also movable into a zero pressure or contact position and then into a pressure-applying position. In the contact position, the garment is effectively trapped between the buck and the movable head for pressing by the selective application of steam or vacuum, while in the pressure-applying position, the head is in high pressure engagement with the buck.

There is an industry need for a pressing machine wherein the pressing head is movable into multiple discrete positions relative to the buck starting from a clear buck position, with the facility to attain such movement substantially automatically and with the ability in the several positions of the pressing head to selectively apply steam and/or vacuum in the usual way. Preferably, the machine incorporating these several positions and automatic control should be of relatively simple mechanical construction and should achieve the several positions and the pressing force by an arrangement of levers and pneumatic controls which are not inordinately complicated and which optimize the relationship of forces such that the machine is capable of mass production manufacture at relatively low cost, is not exceedingly massive and can be serviced with minimum dilficulty and employing relatively unskilled labor.

Broadly, it is an object of the present invention to provide an improved clear buck pressing machine which realizes one or more of the aforesaid objectives. Specifically, it is within the contemplation of the present inven- 3,500,567 Patented Mar. 17, 1970 tion to provide a pressing machine suitable for use in garment manufacturing, dry cleaning and laundering establishments in which the movable pressing head is initially disposed in a clear buck position and which is capable of automatically providing contact and pressureapplying positions for the movable pressing head under operator control such as to facilitate the initial draping of the work on the stationary buck followed by the pressing thereof.

In typical clear buck pressing machines which are currently available on the market, the movable pressing head swings from the clear buck position rearwardly of and behind the stationary buck directly into a position overlying and bearing against the stationary buck, with or without the facility to establish a zero pressure position. In machines of this kind, there is a tendency for the movable pressing head to exert non-uniform pressure across the pressing surface of the stationary buck from the forward edge to the rearward edge thereof. The tendency for non-uniform forces to be exerted by the movable pressing head on the stationary buck manifests itself as a breakdown in padding incident to increased pressure along one edge of the head-buck assembly (usually the forward edge of the pressing head) and decreased pressure on the other edge of the assembly (usually the rearward edge of the pressing head). Additionally, as the movable pressing head swings away from the stationary buck during the opening sequence of the pressing cycle, there is a tendency of the moving head to wipe laterally relative to the stationary buck, which wiping action or lateral displacement often disturbs the condition of the work on the buck.

Accordingly, it is a further object of the present invention to provide a clear buck pressing machine in which the approach and withdrawal of the pressing head from the stationary buck are such as to assure uniform application of pressure and to minimize the tendency to disturb the work.

In accordance with an illustrative embodiment demonstrating objects and features of the present invention, there is provided a pressing machine which comprises a frame having a work table. A stationary buck is mounted on the work table and provides the usual pressing surface. A movable head is mounted on the frame for movement into multiple discrete positions relative to the buck in a pressing cycle, including a clear buck position spaced rearwardly of the buck, a standoff position in spaced confronting relation above the buck, a contact position in contact pressure engagement with the buck and a pressureapplying position in high pressure with the buck. Actuating mechanisms are provided for selectively moving the head through the closing and opening sequence of said pressing cycle with the actuating mechanisms including first means for moving the head from the clear buck position to the standoff position in spaced confronting relation above the buck and second means for moving the head through a vertical and downward thrust relative to the buck to move the head through the closing sequence successively into the contact and pressure-applying positions without changing the confronting relation of the head relative to the buck. Accordingly, uniform pressure is established between the buck and the head during pressing and when the head starts through the opening sequence, there is substantially no sidewise or endwise displacement of the head relative to the buck and attendant displacing or distorting forces on the work draped over the buck. Control means are provided for the actuating mechanisms to move the head through the closing and opening sequences of the pressing cycle.

The above brief description, as well as other objects, features and advantages of the present invention, will be more fully appreciated by reference to the following 3 detailed description of a presently preferred, but nonetheless illustrative embodiment in accordance with the present invention, when taken in conjunction with the accompanying drawings, wherein:

FIG. 1 is a side elevational view of a pressing machine embodying features of the present invention, with parts broken away and shown in phantom, illustrated in the clear buck or maximum open position;

FIG. 2 is a side elevational view similar to FIG. 1, but showing the head of the pressing machine in the standofi position wherein the head is in spaced, confronting and coextensive relation over the stationary buck;

FIG. 3 is a side elevational view similar to FIG. 2, but showing the movable pressing head in a pressureapplying position, having moved through a contact position bearing with substantially zero pressure against the buck;

FIG. 4 is a rear elevational view, with parts broken away, showing the pressure machine in the pressureapplying position of FIG. 3; and,

FIG. 5 is a schematic and diagrammatic view showing the actuating and control mechanisms for achieving the multiple movements of the present pressing machine.

Referringspecifically to the drawings and, in particular, to FIGS. 1-4, inclusive, there is shown a simplified version of a pressing machine embodying features of the present invention and generally designated by the reference numeral 10. The illustrative showing in these drawings has been confined to the basic pressing machine and control. It will be appreciated that such machine and control will be supplemented by mechanisms and a service control for the selective and operator controlled application of steam and/or vacuum to the stationary buck and the movable pressing head. The machine may also be supplemented by other features for pressing machines of this general type, as is generally understood by those skilled in the art.

The pressing machine includes a frame or support 12 including at least two front uprights 14, 16 and two rear uprights 18, 20. The frame or support 12 carries the usual horizontally extending work table 22. Extending above the table 22 in a generally horizontal attitude is the stationary buck 24 which buck is secured to the machine frame 12 by the usual buck-supporting standard 26.

Movably mounted on the frame 12 is a head assembly, generally designated by the reference numeral 28, which includes a C-shaped head lever 30, a movable pressing head 32 and a head aligning and suspending mechanism 34 which adjustably mounts the head 32 on the headsupporting lever. The head 32 is movable on the frame 12 into multiple discrete positions relative to the buck 24 in a pressing cycle which positions include a clear buck position spaced rearwardly of and extending below the buck 24 (as illustrated in FIG. 1), a standofi position in spaced confronting relation coextensive with and above the buck 24 (as illustrated in FIG. 2), a contact position in zero contact or .light contact pressure engagement with the buck (intermediate FIGS. 2 and 3) and a pressure-applying position in high pressure engagement with the buck (as illustrated in FIG. 3).

The C-shaped head supporting lever 30 includes opposed side plates 30a, 30b which are interconnected at their outer margin by rear plate 30c, which, as seen in FIG. 4, is cut away at 30d. At its lower end and straddling the side plates 30a, 30b, the head supporting lever 30 is provided with a horizontal head pivot 36 which has its axis extending in a common vertical plane P with the longitudinal center axis of the stationary buck 24.

Guide means, generally designated by the reference numeral 38, are provided for mounting the horizontal head spivot 36 for displacement in the vertical plane P toward "and away from the stationary buck 24. In this illustrative bodiment, the guide means 38 includes vertical guide 40, 42(see FIG. 4) which are in spaced parallel relation and mounted on the frame 12 by lower and upper cross braces 44, 46. Slidably mounted on the guide rods 40, 42 is a pivot carrier 48 of generally rectangular configuration which includes opposed rearwardly directed bearing sections 48a, 48b which provide opposed bearings for the opposite ends of the head pivot 36. Thus, within the limits of the spacing between the cross braces 44, 46 and the clear space of the guide rods 40, 42, the horizontal head pivot 36 is capable of vertical displacement in the vertical plane P.

The aligning and suspending mechanism 34 which mounts the movable head 32 on the upper end of the C-shaped head supporting lever 30 is of conventional structure. It will suflice to understand that it enables the initial alignment, adjustment and levelling of the movably pressing head 32 to bring the same into a position wherein its longitudinal center line is in the common vertical plane P with the longitudinal center line of the stationary buck 24 after the head moves into the standoff position of FIG. 2 and during the closing and opening sequence from the standoif position through the contact position and the pressure-applying position. Typically, this mechanism includes plural adjustment screws with backup nuts which serve to orient, level and align the pressing head 32 into the desired position relative to the stationary buck 24.

The pneumatically-controlled actuating mechanisms and control of the pressing machine, the operation of which will be fully described in conjunction with FIG. 5, includes a closing piston and cylinder 50, 52 which is operatively connected to the head-supporting lever 30 for pivoting the movable pressing head from the clear buck position, illustrated in FIG. 1 to the standoff position illustrated in FIG. 2. Specifically, the piston is pivotally connected in any conventional fashion to the transverse rib 3012 which extends between side plates 30a, 30b of the head-supporting lever 30 intermediate the ends there of, while the cylinder 52 is pivot-ally mounted at 54 on the base of frame 12. The center of gravity of the head assembly 28, including the lever 30, the head 32 and its suspending mechanism 34, is disposed rearwardly of the head pivot 36 such that the head 32 will pivot in the counterclockwise direction from the standoff position (illustrated in FIG. 2) to the clear buck position (illustrated in FIG. 1) under the influence of gravity when the assembly 28 is free of the restraint imposed by the actuating mechanisms and control of the machine. The head assembly 28 will swing in a counterclockwise direction until the rear plate 300 abuts against adjustable.

bumpers 56, 58 provided at the rear of the base of the machine beneath the C-shaped lever 30, as seen best in FIG. 4.

In order to move the pressing head 32 from the standolf position illustrated in FIG. 2 through the contact pressure position and into the pressure-applying position of FIG. 3, the actuating mechanisms also include a double acting piston and cylinder 60, 62. As it will be fully understood in connection with the description of FIG. 5, the piston and cylinder 60, 62 serve two functions, namely, the counterbalancing of the head assembly 28 and the imparting to the head 32 of downward and upward vertical thrusts to achieve closing and opening movement between the standolf position and the pressure-applying position. The arrangement of the machine is such that the cyinder 62 is mounted immediately beneath the buck-supporting standard 26 on the machine frame 12, with the piston 60 connected to the head pivot 36 at a medial location. Upon actuation of the double acting piston and cylinder 60, 62, a balanced vertical thrust is imparted to the pivot carrier 48 for displacing the axis of the head pivot 36 in the vertical plane P.

In order to aid and assist in assuring that there will be truly perpendicular movement of the head 32 during the closing and opening sequence of the pressing machine cycle between the FIG. 2 and FIG. 3 positions, the headsupporting lever 30 carries a pair of guide rollers 64, 66 which are adapted to bear against the rearward vertical surfaces 18a, 20a of the rear standards 18, 20. These serve as guide tracks when the head 32 is in the standoff position. The guide rollers 64, 66 are journalled outwardly of and on the opposite side plates 30a, 30b, of the head-supporting lever 30 and are adjusted to make contact with the upper ends of the vertical tracks 18a, 20a when the head 24 is in proper alignment in the standoff position (see FIG. 2). Thereafter, the rollers are guided by tracks 18a, 20a as the head 32 moves from the standoff position into the pressure-applying position (see FIGS. 3 and 4).

When the closing cylinder and piston 50, 52 move the head 32 into the standoff position, the vertical head-moving piston and cylinder 60, 62 are actuated by the control which includes an air valve 68. Valve 68 has a pivoted actuator 70 in position to be engaged by an abutment 30 which is appropriately positioned on the'lever 30 to actuate valve 68 when the pressing head 32 moves into the standoff position. The function of this air valve 68 in the overall pneumatic control will be fully understood by reference to FIG. 5.

The pivoting action of the head supporting lever 30 during both the closing and opening sequences of the pressing cycle is hydraulically controlled by the hydraulic check 71 which includes check rod 72 pivotally connected to lever 30 and check cylinder 74 pivotally connected at 76 to the base of the frame'12. The construction of hydraulic check 71 is conventional and its action may be supplemented by the provision of pneumatic snubbers 78, 80 located at both ends of the closing cylinder 52.

By way of review and preliminary to detailed reference to the illustrative pneumatically controlled actuating mechanisms (which are illustrated schematically and diagrammatically in FIG. 5), the sequence of pressing operations includes movement from the clear buck position illustratedin FIG. 1 established by the adjustable bumpers 56, 58 under control of the closing piston and cylinder 50, 52 into the standolf position illustrated in FIG. 2. In such standoff position, perfect vertical alignment is achieved between the movable pressing head 32 and the buck 24. The head pivot 36 occupies the same vertical alignment in the common plane, with the piston 60 of the piston and cylinder assembly 60, 62 being in vertical alignment with the buck-supporting standard and symmetrically connected to the head pivot 36. The vertical closing and opening movement is achieved under control of piston and cylinder 60, 62, with corresponding displacement of the head pivot 36, including the pressure-applying stroke from the contact position (in which the head 32 bears lightly against the buck 24) into the pressure-applying position (wherein the desired degree of pressing pressure is established in accordance with machine adjustment). Significantly, all of the major forces developed in the pressing machine are opposed and balanced relative to each other and no major stress is imparted to the frame 12 of the machine. The mounting of the high pressure cylinder 62 directly beneath the buck-supporting standard 26 assures that the upward thrust imparted by the actuation of the piston and cylinder 60, 62 is opposed by the pressing force applied downwardly on the buck by the pressing head 32 through operation of lever 30. Thus, as a practical matter, frame 12 serves essentially no purpose other than to support the physical weight of the leverage system and to contain the relatively small forces generated by the operation of the closing piston and cylinder 50, 52 in overcoming the weight of the head lever 30 and the pressing head 32.

In FIG. 5, there is shown one pneumatic control for the pressing machine illustrated and described in conjunction with FIGS. l-4, inclusive, which has been found to be eminently satisfactory for achieving the desired coordinated machine functions. It will be appreciated that the illustrated control will be supplemented to provide an appropriate servicing system for the machine, including hand and pedal controls for the application of steam and vacuum selectively to the stationary buck andto the upper pressing head. The control includes a main air supply line 82 which is connected to an appropriate source of air under high pressure, not shown. The main air line 82 is connected to two identical three-way normally closed, pilot-operated, poppet-type air valves 84, 86. These valves include air inlet ports 84a, 86a, air outlet ports 84b, 86b, and pilot ports 84c, 86c. Upon admission of air to the pilot ports 84c, 86c, air from the respective inlet ports 84a, 86a of the valves 84, 86, is transmitted through the valves and to the outlet ports 841i, 86b. At such time as air is cut olf from the pilot ports, the valve closes and the respective inlet ports 84a, 86a are disconnected from the outlet ports 84b, 86b and the valves will be opened through exhaust ports such that any air which has been sent downstream from the valve will be exhausted through the corresponding exhaust ports.

Outlet port 84b of valve 84 is connected via branch pipe 88 to the inlet port 68a of air valve 68 which is of identical construction to valves 84, 86, except that the pilot of the valve is mechanically operated by the pivoted actuator 70 which responds to movement of the pressing head 32 into the standoff position illustrated in FIG. 2. Branch pipe 88 is connected via quick exhaust valve 90 and branch 92 to the'piston head side of closing piston and cylinder 50, 52 which swings the head assembly 28 in the clockwise direction about head pivot 36 from the clear buck position to the standofl? position. The exhaust port 90a of quick exhaust valve 90 is connected to a mufiler 94 which has a built-in flow control which permits suflicient delay in the exhaust of air from the closing cylinder 52 during the opening sequence of the pressing cycle such that the pressing head 32 will first move through its upward thrust into the standoff position prior to the restraint being removed whereupon the head assembly 28 will swing in the counterclockwise direction from the standoff position into the clear buck position under the influence of gravity. Thus, it will be appreciated that actuation of the closing piston and cylinder 50, 52 is controlled via air valve 84, with the necessary porting to atmosphere being achieved via quick release valve 90 and mufiler 94.

As previously explained, the high pressure piston and cylinder 60, 62 are employed to counterbalance the weight of the head assembly 28 in the clear buck position such that no counterbalancing springs are required in the machine. This is achieved by the application, at the appropriate time in the machine cycle, of a reduced air pressure to the lower or piston rod port 62a of the doubleacting piston and cylinder 60, 62. This is achieved by connecting the main air line 82 over adjustable pressurereducing valve 96 to branch line 98 in which a medium pressure is established. This adjusted pressure is used to achieve the desired counterbalancing of the head assembly 28. Specifically, the medium pressure branch line 98 is connected to inlet port 100a of a diaphragm-operated three-way normally open valve 100. Valve 100 has its outlet port 100b connected via a further medium pressure branch line 102 and quick exhaust valve 104 to the piston rod port 62a of cylinder 62. Thus, until the diaphragm-operated, normally open valve 100 is closed, the desired medium pressure is applied from main air line 82 over medium pressure branch lines 98, 102 to the piston and cylinder 60, 62 for the counterbalancing function.

The start of the cycle is controlled by a normally closed three-way cycle-start valve 106 which has its inlet port 106a connected to the main air line 82 and has its outlet port 106b connected via branch line 108, shuttle valve 110 and pilot line 112 to the pilot port 840 of valve 84. The normally closed cycle-start valve 106 is manually operated by the machine operator who depresses a cycle- 7 start lever 113.When this is done, valve 106, which is normally ported to atmosphere over exhaust port 106c, is operated to apply line pressure over outlet 106b, branch line 108, shuttle 110 and pilot line 112 to valve 84. Valve 84, as previously indicated, operates the closing piston and cylinder 50, 52. It also applies line pressure to inlet port 68a of three-way air valve 68 which is normally closed and opens when head 32 arrives in the standoff position. At such time, line pressure is made available at outlet port 68b which is connected via branch. line 114, pressure-reducing valve 116, low pressure branch line 118 and shuttle valve 120 to branch line 122. Line 122 applies pressure to the upper or piston head port 62b of the piston and cylinder 60, 62 via quick release valve 123. It will be appreciated that, depending upon the setting of pressure-reducing valve 116, a desired low pressure is established in branch line 118 which is transmitted via shuttle valve 120 (in the illustrated position) to the upper port 62b of the cylinder ,62. This ,low pressure is effective to move the pressing head 32 from the standoff position into the zero pressure or contact position. The degree of contact pressure can be changed by appropriate adjustment of valve 116. Concurrent with the introduction of the desired rate of air flow to achieve contact pressure to low pressure branch 118, air from the outlet port 68 also is applied via branch 124, shuttle valve 126 and branch 128 to the diaphragm port 1001: of valve 100 to close this normally open valve. This will connect the medium pressure line 102 to exhaust port 100d. Thus, when high pressure air is admitted to the diaphragm port 100a of valve 100,this valve is operated so that no further medium pressure air can be transmitted through thevalve to the lower or piston rod port 62a of piston and cylinder 60, 62..The air that has been fed through diaphragm control valve 100 to the'high pressure piston and cylinder 60, ,62 is exhausted through the exhaust port 100d of valve 6 100 and the exhaust. port of the quick exhaust valve 104. When this supply of medium pressure air is exhausted there is nothing to. counterbalance the upper head and it is permitted to settle on the buck under control 'ofthe pressure established via contact pressure regulator 116.

.The final aspect of the control involves an understandingof the function of valve 86, which is identical to valvet84 and functions in the same manner, but under control of a hand operated, normally closed three-way valve. 130 which is actuated by the high pressure-applying lever 132. Valve 130 has its inlet port 130a connected to the main air line82 and its outlet port 130b connected to pilot line 134 which is connected to pilot port 86c of valve 86. Thus, opening of valve 86 and the connection of its inlet port 86a to its outlet port 86b and the corresponding application of main line pressure to branch line 136 is controlled by valve 130 and lever 132. Accordingly, when the machine operator desires to move the pressing head from the zero contact or light pressure position, high pressure-applying lever 132 is manipulated to actuate valve 86 to apply line pressure via outlet port 86b of valve 86 to branch line 136. Pressure in branch line 136 is effective via branch 138 to shift shuttle valve to a posi tion wherein line pressure is supplied to pilot line 112 to keep valve 184 open and to apply line pressure to branch line 88. Also, the application of line pressure to branch line 136 is effective via shuttle valve 120 to apply line pressure to branch line 122. This applies the desired high pressure to the upper or piston head port 62b of piston and cylinder 60, 62 and establishes the pressure-applying position of the pressing head 32. Finally, branch line 138 is connected via further branch line 140' and shuttle valve 126 to maintain continued porting of diaphragm-operated valve 100 to atmosphere to remove the medium pressure {from the lower port 62a. of. the piston and cylinder 60, :62. This is required since valve 68 closes once the head 01; 36 moves downward y when abutment 30 is cleared from the position of engaging the actuator 70' for the pilot of valve 68. I

Upon release of the high pressure-applying lever 132, all of the pneumatic circuits will reverse themselves. High pressure air is released from the upper port 62b and medium pressure air is admitted to the lower port 62a which serves to elevate the pressing head 32 to the standoff position. At the appropriate time in the cycle, high pressure air is also exhausted from the closing cylinder 52 over quick relaese valve and exhaust mufller 94. When the head 32 is returned to the standoff position, the system is conditioned such that the force of gravity will take over to restore the head assembly 28 to the clear buck position, with the desired counterbalancing 24 being exerted by the re-establishment of the medium pressure at the lower port 62a of piston and cylinder 60, 62.

From the foregoing, it will be appreciated that there has been provided a pressing machine which is of essentially simple construction, yet achieves the desired coordinating functions in a highly economical and efficient manner.

What is claimed is:

1. A pressing'machine comprising a frame having a work table, a stationary buck on said work table, a movable head mounted on said frame for movement into multiple discrete positions relative to said buck in a pressing cycle, including a clear buck position spaced rearwardly of said buck, a standoff position in spaced-confronting relation above said buck; a contact position in contact pressure engagement with said buck and a pressure-applying position in high pressure engagement with said buck, actuating mechanisms for selectively moving said head through the closing and opening sequence of said pressing cycle, said actuating mechanisms including first means for moving said head from said clear buck position to, said standoff position in spaced-confronting relation above said buck and secondmeans for moving said head through a vertical and downward thrust relative to said buck to move said head through said closingsequence successively into said contact and pressure-applying position without changing the confronting relation of saidhead relative to said buck whereby there is no sidewise or endwise displacement of said head relative to buck and control means for said actuating mechanisms for moving said head through said closing sequence.

2. A pressing machine according to claim 1 including a head-supporting lever and means mounting said headsupporting lever on a horizontal head pivot with the pivot axis disposed in a common vertical plane with the longi: tudinal center line of said buck and the center line of said head when the latter is in said standoff, contact and res sure-applying positions.

3. A pressing machine according to claim 2 wherein said first means of said actuating mechanisms includes a closing piston and cylinder operatively connected to said head-supporting lever for pivoting the latter to move said head from said clear buck position to said standoff position.

4. A pressing machine according to claim 2 including means mounting said head pivot for vertical movement such that said first axis is capable of moving in said vertical plane and wherein said second means is operative to move said head pivot to actuate said head through said vertical and downward thrust in said closing sequence.

5. A pressing machine according to claim 4 wherein said second means includes a combined contact and high pressure piston and cylinder operativelty connected to said head pivot.

6. A pressing machine according to claim 5 wherein said cylinder is mounted on said frame beneath said buck with the axis of its piston in said vertical plane, said piston being operatively connected to said head pivot along a transverse center line common to said buck.

7. A pressing machine according to claim 1 wherein said opening sequence includes moving said head through a vertical and upward thrust from said contact position to said standoff position such that said head will clear said buck in a vertical motion and thereby avoid transmission of sidewise displacement forces to work draped on said buck.

8. A pressing machine according to claim 1 including a head-supporting lever having a horizontal head pivot on said frame and mounting said head for pivotal movement betweetn said clear buck position and said standoff position, the longitudinal center lines of said buck and said head when in said standoff position being in a common vertical plane with said head pivot and the center of gravity of said head-supporting lever and head being disposed rearwardly of said head pivot such that said head will pivot from said standoff position to said clear buck position under the influence of gravity when free of the restraint imposed by said actuating mechanisms and the control means thereof.

9. A pressing machine according to claim 8 wherein said second means of said actuating mechanisms includes a double-acting piston and cylinder and said control means is arranged to apply pressure to the end of said cylinder which is effective to counteract the force of gravity acting on said head and head lever and counterbalance said head and head lever.

10. A pressing machine according to claim 9 wherein said first means of said actuating mechanisms includes a single acting piston and cylinder for moving said head from said clear buck position to said standoff position against the influence of gravity.

11. A pressing machine comprising a frame having a work table, a stationary buck mounted on said work table and having a longitudinal center axis, a C-shaped headsupporting lever, a horizontal head pivot on the lower end of said lever having its axis extending in a common vertical plane with said longitudinal center axis of said buck, guide means mounting said head pivot on said frame for displacement in said vertical plane toward and away from said buck, a pressing head mounted on the upper end of said lever and movable from a clear buck position spaced rearwardly of said buck to a standofl position overlying said buck in which its longitudinal center line is in said vertical plane, the center of gravity of said lever and head being disposed rear-wardly of the axis of said head pivot such that said head will move under the influence of gravity from said standoif position to said clearance position when freed from restraint and actuating mechanisms including means operatively connected to said lever for pivoting said head from said clear buck position to said standoff position against the force of gravity.

same downwardly in said vertical plane to move said head through a downward thrust into a contact position with said buck, the longitudinal center axis of said head remaining in said vertical plane during movement of said head from said standoff position to said contact position.v

lever for pivoting the latter to move said head from said clear buck position to said standoff position.

15. A pressing machine according to claim 14 wherein said actuating mechanisms include a combined contact and high pressure piston and cylinder operatively con- I nected to said head pivot.

12. A pressing machine according to claim 11 wherein 16. A pressing machine according to claim 15 wherein said cylinder is mounted on said frame beneath said buck with the axis of its piston in said vertical plane, said piston being operatively connected to said head pivot along a transverse center line common to said buck.

17. A pressing machine according to claim 11 wherein said pressing head has an opening sequence including moving said head through a vertical and upward thrust from said contact position to said standoff position such that said head will clear said buck in a vertical motion and thereby avoid transmission of sidewise displacement forces to work draped on said buck.

18. A pressing machine according to claim 11 wherein said actuating mechanisms include pneumatic means which is effective to counteract the force of gravity acting on said head and head lever and counterbalance said head and head lever.

References Cited UNITED STATES PATENTS 2,483,461 10/1949 Howlett 3835 2,644,254 7/ 3 Schultz 3841 X 2.599,238 6/1952 Dayton 3835 2,728,152 12/1955 Campbell 38-35 3,279,106 10/1966 Tucker 38-40 3,414,992 12/ 1968 Dachtler 38-41 MERVIN STEIN, Primary Examiner GEORGE V. LARKIN, Assistant Examiner U.S. Cl. X.R. 38-41 

